US4580593A - Disk valve for corrosive fluids - Google Patents

Disk valve for corrosive fluids Download PDF

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Publication number
US4580593A
US4580593A US06/752,589 US75258985A US4580593A US 4580593 A US4580593 A US 4580593A US 75258985 A US75258985 A US 75258985A US 4580593 A US4580593 A US 4580593A
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Prior art keywords
sealing
disk
bushes
covering
disk valve
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Expired - Fee Related
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US06/752,589
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Gunter Herberholz
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K27/00—Construction of housing; Use of materials therefor
    • F16K27/02—Construction of housing; Use of materials therefor of lift valves
    • F16K27/0209—Check valves or pivoted valves
    • F16K27/0218—Butterfly valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K1/00—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces
    • F16K1/16—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces with pivoted closure-members
    • F16K1/18—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces with pivoted closure-members with pivoted discs or flaps
    • F16K1/22—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces with pivoted closure-members with pivoted discs or flaps with axis of rotation crossing the valve member, e.g. butterfly valves
    • F16K1/226—Shaping or arrangements of the sealing
    • F16K1/2268—Sealing means for the axis of rotation
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/6851—With casing, support, protector or static constructional installations
    • Y10T137/7036—Jacketed

Definitions

  • the invention relates to a disk valve for corrosive fluids comprising a tubular metal housing lined with a hard-elastic, unpadded coating and a throttle disk with a hard-sealing, unpadded covering being made up of hard synthetic resin and being of a minimum thickness of three millimeters.
  • the throttle disk is attached to two pivot pins extending through said coating and said metal housing and the throttle disk is sealing said metal housing in a transverse plane comprising the axis of said pivot pins.
  • the sealing peripheral surface of said disk covering is profiled as a symmetrical spherical sector and the pivot pins are directly enclosed by separate, hard-elastic sealing bushes, the sealing bushes seating on the covered throttle disk and being separately adjustable.
  • a disk valve is known with a tubular metal housing lined by a hard-elastic, unpadded plastic coating and with a throttle disk provided with a hard-sealing covering of tantalum.
  • the pivot pins of that throttle disk are enclosed by separate, hard-elastic sealing bushes directly seating with their front ends on the throttle disk.
  • the throttle disk of a disk valve can be additionally provided with a covering of perfluoralkoxy with a minimum thickness of three millimeters so that the possible temperature range is considerably enlarged.
  • a creeping of the disk covering and thus slight leakages are possible. Nevertheless, such leakages with only a minimal quantity result in the destruction of the pivot pins.
  • the sealing bushes are respectively pressed with wedge-shaped front ends into V-shaped annular grooves of the disk covering.
  • the sealing effect at the front ends of the sealing bushes considerably improves and is even maintained, if the covering of the throttle disk evades a little bit by creeping.
  • FIG. 1 is a front view of a first embodiment of a disk valve
  • FIG. 2 is a sectional view of the disk valve taken along the line II--II in FIG. 1;
  • FIG. 3 is a sectional view of the disk valve taken along the line III--III in FIG. 1;
  • FIG. 4 shows the lower sealing bushes of the disk valve according to a partial section IV in FIG. 3;
  • FIG. 5 is an enlarged view illustrating the combination of the V-groove ofthe disk covering and the wedge-shaped front end of a sealing bush according to a partial section V in FIG. 4;
  • FIG. 6 is an enlarged view of the transition point between two sealing bushes according to a partial section VI in FIG. 4;
  • FIG. 7 illustrates a second embodiment of a disk valve in an analogous view as in FIG. 4.
  • FIGS. 1 to 6 show a disk valve for corrosive fluids with a tubular metal housing 1 lined with a hard-elastic, unpadded plastic coating 4, e.g. of polytetrafluor ethylene.
  • the metal housng 1 is divided into two parts 2, 3 at its horizontal median plane and is held together by screws 50, cg. FIG. 1 and 2.
  • the inner opening of the tubular metal housing 1 can be closed by a throttle disk 5 consisting of a steel core 19 with a hard-sealing, unpadded covering 23, e.g. of sintered perfluoralkoxy, of a thickness of at least millimeters.
  • the throttle disk 5 is pivotally attached to two pivot pins 9, 10 extending through the coating 4 and the housing 1, the upper pivot pin 9 being joint for a common rotation to the throttle disk 5 by a square bar 11 and to an actuating lever 8 by an adjusting feather 12.
  • the closed throttle disk 5 seals the metal housing 1 in a transverse plane comprising the axis of the pivot pins 9, 10, wherein the sealing peripheral surface 24 is profiled like a symmetrical spherical sector as indicated by dot-dash circles in the FIGS. 2 and 3.
  • the breadth of the peripheral surface 24 continuously diminishs from the upper and lower pivot bearings of the disk 5 to its horizontal medium plane, whereby on the one hand an optimal sealing and on the other hand an easy operation of the throttle disk 5 are achieved.
  • the front faces of the throttle disk 5 are smoothbore profiles so that the sedimentation of abrasive substances is prevented.
  • the pivot pins 9, 10 are enclosed at their bearings by separate, hard-elastic sealing bushes 13, 14, 29, 30 preferably consisting of polytetrafluor ethylene.
  • the inner sealing bush 14--and accordingly the bush 13 of the upper bearing-- is pressed with a wedge-shaped front end 31 into a V-shaped annular groove 32 of the covering 23 of the disk 5.
  • outer sealing bushes 29, 30 are axially added to each of the inner sealing bushes 13, 14, the inner sealing bushes 13, 14 having V-shaped grooves 33 at their rear ends, and the outer sealing bushes 39, 40 being pressed with their wedge-shaped front ends 34 into said grooves 33.
  • Each set of the bushes 13, 29 respectively 14, 30 can be adjusted by rearward abutment nuts 15, 16, wherein metal bearing bushes 17 are interposed between the sealing bushes 13, 29 respectively 14, 30 and the nuts 15, 16. Due to these bearing bushes 17, the sealing bushes 13, 29, 14, 30 only cover a short axial distance which is really necessary for a sufficient sealing of the housing 1.
  • the radial enlargement of the sealing bushes 13, 29, 14, 30 by an axial pressing causes such a low clamping effect that the throttle disk 5 can easily be rotated.
  • the bearing bushes 17 exactly guide the pivot pins 9, 10.
  • the wedge angles ⁇ of the front ends 31, 34 of the sealing bushes 13, 14, 29, 30 are greater than the respective groove angles ⁇ of the grooves 32, 33.
  • a high pressing of the sealing surfaces is even obtained, if for example the covering 23 of the disk 5 laterally evades by creeping.
  • the wedge edges 39, 40 are beveled so that a well defined correlation of the sealing surfaces is acheived, even in case of manufacturing variations.
  • these measures make possible an axisl adjustment of the sealing bushes 13, 14, 29, 30 by the abutment nuts 15, 16.
  • FIG. 7 is principally identical to the embodiment of the FIGS. 1 to 6. The only difference consists in the detail that the transition point 41 between the two sealing bushes 42, 43 is within the reach of the coating 4 of the housing 1.
  • an axial pressing causes a greater radial enlargement of the bushes 42, 43.
  • the penetration of corrosive fluids is stopped at the latest at the transition point 41 so that the metal housing is safely proteced.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Lift Valve (AREA)
  • Sliding Valves (AREA)

Abstract

The invention relates to a disk valve for corrosive fluids comprising a tubular metal housing lined with a hard-elastic, unpadded coating and a throttle disk with a hard-sealing, unpadded covering being made up of hard synthetic resin and being of a minimum thickness of three millimeters. The throttle disk is attached to two pivot pins extending through said coating and said metal housing and the throttle disk is sealing said metal housing in a transverse plane comprising the axis of said pivot pins. The pivot pins are directly enclosed by separate, hard-elastic sealing bushes seating on the covered throttle disk and being separately adjustable. In order to provide a disk valve which can be applied for a large temperature range and which has no leakages at the sealing bushes as well, the sealing bushes are respectively pressed with wedge-shaped front ends into V-shaped annular grooves of the disk covering.

Description

The invention relates to a disk valve for corrosive fluids comprising a tubular metal housing lined with a hard-elastic, unpadded coating and a throttle disk with a hard-sealing, unpadded covering being made up of hard synthetic resin and being of a minimum thickness of three millimeters. The throttle disk is attached to two pivot pins extending through said coating and said metal housing and the throttle disk is sealing said metal housing in a transverse plane comprising the axis of said pivot pins. The sealing peripheral surface of said disk covering is profiled as a symmetrical spherical sector and the pivot pins are directly enclosed by separate, hard-elastic sealing bushes, the sealing bushes seating on the covered throttle disk and being separately adjustable.
By the German Pat. No. 27 58 690 a disk valve is known with a tubular metal housing lined by a hard-elastic, unpadded plastic coating and with a throttle disk provided with a hard-sealing covering of tantalum. The pivot pins of that throttle disk are enclosed by separate, hard-elastic sealing bushes directly seating with their front ends on the throttle disk. By this combination of the materials of the disk-covering and of the sealing bushes, the penetration of corrosive fluids to the pivot pins is safely prevented. But because of the different thermal extension of the plastic coating of the housing and the metal throttle disk, the known disk valve can only be applied for a quite limited temperature range.
According to the German Offenlegungsschrift No. 33 13 904, the throttle disk of a disk valve can be additionally provided with a covering of perfluoralkoxy with a minimum thickness of three millimeters so that the possible temperature range is considerably enlarged. But because of the axial pressing of the sealing bushes, a creeping of the disk covering and thus slight leakages are possible. Nevertheless, such leakages with only a minimal quantity result in the destruction of the pivot pins.
It is an object of this invention to provide a disk valve which can be applied for a large temperature range and which has no leakages at the sealing bushes as well. According to an advantageous feature of the invention, the sealing bushes are respectively pressed with wedge-shaped front ends into V-shaped annular grooves of the disk covering. Thus, the sealing effect at the front ends of the sealing bushes considerably improves and is even maintained, if the covering of the throttle disk evades a little bit by creeping.
The invention will now be described with reference to the accompanying drawings illustrating two preferred embodiments of the disk valve according to the present invention.
FIG. 1 is a front view of a first embodiment of a disk valve;
FIG. 2 is a sectional view of the disk valve taken along the line II--II in FIG. 1;
FIG. 3 is a sectional view of the disk valve taken along the line III--III in FIG. 1;
FIG. 4 shows the lower sealing bushes of the disk valve according to a partial section IV in FIG. 3;
FIG. 5 is an enlarged view illustrating the combination of the V-groove ofthe disk covering and the wedge-shaped front end of a sealing bush according to a partial section V in FIG. 4;
FIG. 6 is an enlarged view of the transition point between two sealing bushes according to a partial section VI in FIG. 4; and
FIG. 7 illustrates a second embodiment of a disk valve in an analogous view as in FIG. 4.
The FIGS. 1 to 6 show a disk valve for corrosive fluids with a tubular metal housing 1 lined with a hard-elastic, unpadded plastic coating 4, e.g. of polytetrafluor ethylene. The metal housng 1 is divided into two parts 2, 3 at its horizontal median plane and is held together by screws 50, cg. FIG. 1 and 2.
The inner opening of the tubular metal housing 1 can be closed by a throttle disk 5 consisting of a steel core 19 with a hard-sealing, unpadded covering 23, e.g. of sintered perfluoralkoxy, of a thickness of at least millimeters. The throttle disk 5 is pivotally attached to two pivot pins 9, 10 extending through the coating 4 and the housing 1, the upper pivot pin 9 being joint for a common rotation to the throttle disk 5 by a square bar 11 and to an actuating lever 8 by an adjusting feather 12.
The closed throttle disk 5 seals the metal housing 1 in a transverse plane comprising the axis of the pivot pins 9, 10, wherein the sealing peripheral surface 24 is profiled like a symmetrical spherical sector as indicated by dot-dash circles in the FIGS. 2 and 3. As a comparison of the FIGS. 2 and 3 clearly demonstrates, the breadth of the peripheral surface 24 continuously diminishs from the upper and lower pivot bearings of the disk 5 to its horizontal medium plane, whereby on the one hand an optimal sealing and on the other hand an easy operation of the throttle disk 5 are achieved. The front faces of the throttle disk 5 are smoothbore profiles so that the sedimentation of abrasive substances is prevented.
The pivot pins 9, 10 are enclosed at their bearings by separate, hard- elastic sealing bushes 13, 14, 29, 30 preferably consisting of polytetrafluor ethylene. As shown in the FIGS. 4 to 6 for the example of the lower bearing, the inner sealing bush 14--and accordingly the bush 13 of the upper bearing--is pressed with a wedge-shaped front end 31 into a V-shaped annular groove 32 of the covering 23 of the disk 5. Thus, an excellent radial sealing of the pivot pins 9, 10 is achieved. In order to compensate excentricities due to the manufacture, outer sealing bushes 29, 30 are axially added to each of the inner sealing bushes 13, 14, the inner sealing bushes 13, 14 having V-shaped grooves 33 at their rear ends, and the outer sealing bushes 39, 40 being pressed with their wedge-shaped front ends 34 into said grooves 33. Each set of the bushes 13, 29 respectively 14, 30 can be adjusted by rearward abutment nuts 15, 16, wherein metal bearing bushes 17 are interposed between the sealing bushes 13, 29 respectively 14, 30 and the nuts 15, 16. Due to these bearing bushes 17, the sealing bushes 13, 29, 14, 30 only cover a short axial distance which is really necessary for a sufficient sealing of the housing 1. Thus, the radial enlargement of the sealing bushes 13, 29, 14, 30 by an axial pressing causes such a low clamping effect that the throttle disk 5 can easily be rotated. Furthermore, the bearing bushes 17 exactly guide the pivot pins 9, 10.
As the FIGS. 5 and 6 illustrate, the wedge angles β of the front ends 31, 34 of the sealing bushes 13, 14, 29, 30 are greater than the respective groove angles α of the grooves 32, 33. By this way, a high pressing of the sealing surfaces is even obtained, if for example the covering 23 of the disk 5 laterally evades by creeping. Moreover, the wedge edges 39, 40 are beveled so that a well defined correlation of the sealing surfaces is acheived, even in case of manufacturing variations. Furthermore, these measures make possible an axisl adjustment of the sealing bushes 13, 14, 29, 30 by the abutment nuts 15, 16. Because of the combination of the disk covering 23 of perfluoralkoxy and the sealing bushes 13, 14 of the somewhat softer polytetrafluor ethylene, mainly the front ends 31 of the sealing bushes 13, 14 wear off, whereas the disk covering 23 is factually preserved. Thus after several adjustment of the abutment nuts 15, 16, only the cheap sealing buses 13, 14, 29, 30 have to be exchanged, while the main components of the disk valve have a very long working life.
The embodiment of FIG. 7 is principally identical to the embodiment of the FIGS. 1 to 6. The only difference consists in the detail that the transition point 41 between the two sealing bushes 42, 43 is within the reach of the coating 4 of the housing 1. By this arrangement of the V-groove 33 and the wedge-shaped front end 34 an axial pressing causes a greater radial enlargement of the bushes 42, 43. Thus, the penetration of corrosive fluids is stopped at the latest at the transition point 41 so that the metal housing is safely proteced.

Claims (9)

What I claim is:
1. A disk valve for corrosive fluids comprising
a tubular metal housing lined with a hard-elastic, unpadded coating,
a throttle disk having a hard-sealing, unpadded covering,
two pivot pins extending through said coating and said metal housing,
said throttle disk being attached to said pivot pins, and sealing said metal housing in a transverse plane comprising the axis of said pivot pins,
said covering having a sealing peripheral surface profiled as a symmetrical spherical sector and having V-shaped annular grooves each surrounding one of said pivot pins,
separate, hard-elastic sealing bushes enclosing directly the pivot pins and having wedge-shaped front ends, which are adjustable against the covering,
wherein said covering of the throttle disk is made up of hard synthetic resin and is of a minimum thickness of three millimeters,
and wherein said sealing bushes are respectively pressed with the wedge-shaped front ends into the V-shaped annular grooves of said disk covering.
2. A disk valve according to claim 1, further comprising rearward abutment nuts for adjusting the sealing bushes and bearing bushes respectively interposed between said sealing bushes and said abutment nuts.
3. A disk valve according to claim 1, wherein each pivot pin is enclosed by at least two sealing bushes axially installed in series and wherein the inner sealing bushes have V-shaped grooves at their rear ends and the respective outer bushes have wedge-shaped front ends pressed into said grooves.
4. A disk valve according to claim 3, wherein the transition point between the two sealing bushes is within the reach of the coating of the metal housing.
5. A disk valve according to claim 1, wherein the wedge angles at the front ends of the sealing bushes are greater than the respective groove angles at the covering of the throttle disk.
6. A disk valve according to claim 3, wherein the wedge angles at the front ends of the outer sealing bushes are greater than the respective groove angles at the rear ends of the inner sealing bushes.
7. A disk valve according to claim 5, wherein the edges of the wedge-shaped front ends are beveled.
8. A disk valve according to claim 6, wherein the edges of the wedge-shaped front ends are beveled.
9. A disk valve according to claim 1, wherein the covering of the throttle disk is made up of perfluoralkoxy and the sealing bushes consist of polytetrafluor ethylene.
US06/752,589 1984-07-06 1985-07-08 Disk valve for corrosive fluids Expired - Fee Related US4580593A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19843424924 DE3424924A1 (en) 1984-07-06 1984-07-06 BUTTERFLY VALVE FOR AGGRESIVE FLOW MEDIA
DE3424924 1984-07-06

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EP (1) EP0166855B1 (en)
AT (1) ATE35035T1 (en)
DE (2) DE3424924A1 (en)

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4674528A (en) * 1985-09-11 1987-06-23 Kitz Corporation Butterfly valve
US5409654A (en) * 1993-08-05 1995-04-25 Nibco Inc. Method of reaction injection molding a valve
GB2284647A (en) * 1993-11-30 1995-06-14 Sigeval S A Butterfly valve
US5971358A (en) * 1998-06-11 1999-10-26 Penn Troy Machine Co., Inc. Gate assembly for a double disk gate valve
EP0886089A3 (en) * 1997-06-18 1999-12-29 Bopp & Reuther Armaturen GmbH Butterfly valve
US20020175308A1 (en) * 2001-05-28 2002-11-28 Klaus Leyendecker Flap device
US20070080314A1 (en) * 2005-10-06 2007-04-12 Arvin Technologies, Inc. Exhaust valve bushing
US20120007314A1 (en) * 2009-03-27 2012-01-12 Cameron International Corporation Full bore compression sealing method
US20130284963A1 (en) * 2011-10-27 2013-10-31 Aegis Flow Technologies, L.L.C. Butterfly Valve and Stem Sealing Assembly
CN104879509A (en) * 2015-05-21 2015-09-02 大众阀门集团有限公司 Eccentric stop valve
US11525516B2 (en) * 2015-10-07 2022-12-13 Fisher Controls International Llc Valve body insert apparatus and related methods

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1991715A (en) * 1932-07-29 1935-02-19 Harley T Wheeler Packing set shape
US3438388A (en) * 1965-10-19 1969-04-15 Duriron Co Fully lined valve
US3958595A (en) * 1974-11-22 1976-05-25 Dresser Industries, Inc. Corrosion resistant valve construction
US4283062A (en) * 1979-12-26 1981-08-11 Cincinnati Milacron Inc. Hydraulic injection molding machine stuffing box
US4291863A (en) * 1978-10-17 1981-09-29 Jean Gachot Antifriction device for a valve control shaft

Family Cites Families (9)

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US3096070A (en) * 1956-09-06 1963-07-02 Rockwell Mfg Co Plug valve construction
US3334650A (en) * 1964-03-12 1967-08-08 Acf Ind Inc Valve
US3778028A (en) * 1972-08-02 1973-12-11 Dore Co John L Lined butterfly valve
FR2255522B1 (en) * 1973-12-19 1982-11-12 Amri
DE2648519C2 (en) * 1976-10-27 1986-04-17 Josef 6200 Wiesbaden Nemetz Butterfly valve
ES466092A1 (en) * 1977-04-01 1979-01-01 Asahi Organic Chem Ind Butterfly valve assembly
DE2758690C2 (en) * 1977-12-29 1982-09-30 Günter 5600 Wuppertal Herberholz Butterfly valve for aggressive flow media
DE2925004A1 (en) * 1979-06-21 1981-01-15 Pfeiffer Chemie Armaturen Shut=off valve for aggressive media - has chevron seals with lining and facings entirely of PTFE
DE3313904A1 (en) * 1983-04-16 1984-10-25 Günter 5830 Schwelm Herberholz Shut-off flap for aggressive through flowing media

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1991715A (en) * 1932-07-29 1935-02-19 Harley T Wheeler Packing set shape
US3438388A (en) * 1965-10-19 1969-04-15 Duriron Co Fully lined valve
US3958595A (en) * 1974-11-22 1976-05-25 Dresser Industries, Inc. Corrosion resistant valve construction
US4291863A (en) * 1978-10-17 1981-09-29 Jean Gachot Antifriction device for a valve control shaft
US4283062A (en) * 1979-12-26 1981-08-11 Cincinnati Milacron Inc. Hydraulic injection molding machine stuffing box

Cited By (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4674528A (en) * 1985-09-11 1987-06-23 Kitz Corporation Butterfly valve
US5409654A (en) * 1993-08-05 1995-04-25 Nibco Inc. Method of reaction injection molding a valve
US5503544A (en) * 1993-08-05 1996-04-02 Nibco Inc. Mold for reaction injection molding of a valve
US5509441A (en) * 1993-08-05 1996-04-23 Nibco Inc. Reaction injection molded valve
GB2284647A (en) * 1993-11-30 1995-06-14 Sigeval S A Butterfly valve
EP0886089A3 (en) * 1997-06-18 1999-12-29 Bopp & Reuther Armaturen GmbH Butterfly valve
US5971358A (en) * 1998-06-11 1999-10-26 Penn Troy Machine Co., Inc. Gate assembly for a double disk gate valve
US6254060B1 (en) * 1998-06-11 2001-07-03 Penn Troy Machine Company, Inc. Gate assembly for a double disk gate valve
US20020175308A1 (en) * 2001-05-28 2002-11-28 Klaus Leyendecker Flap device
US20070080314A1 (en) * 2005-10-06 2007-04-12 Arvin Technologies, Inc. Exhaust valve bushing
US20120007314A1 (en) * 2009-03-27 2012-01-12 Cameron International Corporation Full bore compression sealing method
US10053946B2 (en) * 2009-03-27 2018-08-21 Cameron International Corporation Full bore compression sealing method
US20130284963A1 (en) * 2011-10-27 2013-10-31 Aegis Flow Technologies, L.L.C. Butterfly Valve and Stem Sealing Assembly
US9512926B2 (en) * 2011-10-27 2016-12-06 Aegis Flow Technologies, L.L.C. Butterfly valve and stem sealing assembly
CN104879509A (en) * 2015-05-21 2015-09-02 大众阀门集团有限公司 Eccentric stop valve
US11525516B2 (en) * 2015-10-07 2022-12-13 Fisher Controls International Llc Valve body insert apparatus and related methods

Also Published As

Publication number Publication date
ATE35035T1 (en) 1988-06-15
EP0166855B1 (en) 1988-06-08
DE3424924A1 (en) 1986-02-06
EP0166855A2 (en) 1986-01-08
DE3563256D1 (en) 1988-07-14
EP0166855A3 (en) 1986-09-03

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Effective date: 19900408